CN104136807A - Multi-stage planetary vehicle transmission - Google Patents
Multi-stage planetary vehicle transmission Download PDFInfo
- Publication number
- CN104136807A CN104136807A CN201380010299.2A CN201380010299A CN104136807A CN 104136807 A CN104136807 A CN 104136807A CN 201380010299 A CN201380010299 A CN 201380010299A CN 104136807 A CN104136807 A CN 104136807A
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- China
- Prior art keywords
- gear
- switching member
- axle
- planet
- planetary gear
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- 230000005540 biological transmission Effects 0.000 title claims abstract description 16
- 238000010276 construction Methods 0.000 claims description 6
- 238000010586 diagram Methods 0.000 description 5
- 230000008878 coupling Effects 0.000 description 3
- 238000010168 coupling process Methods 0.000 description 3
- 238000005859 coupling reaction Methods 0.000 description 3
- 230000000694 effects Effects 0.000 description 3
- 241000446313 Lamella Species 0.000 description 2
- 230000002349 favourable effect Effects 0.000 description 2
- 230000015572 biosynthetic process Effects 0.000 description 1
- 230000001419 dependent effect Effects 0.000 description 1
- 239000012530 fluid Substances 0.000 description 1
- 230000000977 initiatory effect Effects 0.000 description 1
- 239000006247 magnetic powder Substances 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 238000005457 optimization Methods 0.000 description 1
Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
- F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
- F16H3/62—Gearings having three or more central gears
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
- F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
- F16H3/62—Gearings having three or more central gears
- F16H3/66—Gearings having three or more central gears composed of a number of gear trains without drive passing from one train to another
- F16H3/666—Gearings having three or more central gears composed of a number of gear trains without drive passing from one train to another with compound planetary gear units, e.g. two intermeshing orbital gears
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H2200/00—Transmissions for multiple ratios
- F16H2200/003—Transmissions for multiple ratios characterised by the number of forward speeds
- F16H2200/0065—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratios comprising nine forward speeds
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H2200/00—Transmissions for multiple ratios
- F16H2200/003—Transmissions for multiple ratios characterised by the number of forward speeds
- F16H2200/0069—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratios comprising ten forward speeds
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H2200/00—Transmissions for multiple ratios
- F16H2200/20—Transmissions using gears with orbital motion
- F16H2200/2002—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears
- F16H2200/2012—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears with four sets of orbital gears
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H2200/00—Transmissions for multiple ratios
- F16H2200/20—Transmissions using gears with orbital motion
- F16H2200/203—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes
- F16H2200/2046—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes with six engaging means
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Structure Of Transmissions (AREA)
Abstract
Disclosed is a multi-stage planetary vehicle transmission comprising a housing (9) in which four planetary gear sets (RS1, RS2, RS3, RS4), a plurality of shafts (1, 2, 3, 4, 5, 6, 7, 8, 8A, 8B, 8C, 8D) , and six shifting elements (A, B, C, D, E, F) are arranged which allow a plurality of gear stages to be implemented upon actuation thereof. The first shaft (1), as an input element (An), is directly connected or can be indirectly connected to the sun gear (SO3) of the third planetary gear set (RS3), can be indirectly connected to the sun gear (SO1) of the first planetary gear set (RS1), can be indirectly connected to the planet gear carrier (PT1) of the first planetary gear set (RS1), and can be indirectly connected to the planet gear carrier (PT2) of the second planetary gear set (RS2). The second shaft (2), as an output element (Ab), is directly connected to the annulus (HO4) of the fourth planetary gear set (RS4) and is directly connected or can be indirectly connected to the planet gear carrier (PT3) of the third planetary gear set (RS3). The sun gear (SO1) and the planet gear carrier (PT1) of the first planetary gear set (RS1) as well as the sun gear (SO4) of the fourth planetary gear set (RS4) can each be connected to the housing (9), the annulus (HO 1) of the first planetary gear set (RS1) being connected to the planet gear carrier (PT4) of the fourth planetary gear set (RS4) and being connectable or connected to the sun gear (SO2) of the second planetary gear set (RS2), and the annulus (HO2) of the second planetary gear set (RS2) and the annulus (HO3) of the third planetary gear set (RS3) being connectable or connected to one another.
Description
Technical field
The present invention relates to the multiple-speed gear-box of the planetary gear construction mode for vehicle of the type of a kind of basis specific definition in claim 1 preamble.
Background technique
A kind of multiple-speed gear-box of the planetary gear construction mode for vehicle is for example disclosed by patent documentation US7887453B2.This multiple-speed gear-box comprises four planetary gear set and six switching members, reverses gear to realize nine forward gears and one.From the gearshift sketch of this known multiple-speed gear-box, in order to realize only wherein two switching members of closure of each gear difference.Therefore the chip switching member based on opening produces undesirable towing loss.
In addition known by switching member locate be easy to approach, as be positioned at outside be favourable and therefore can be simpler and/or lossless arrange hydraulic pressure and/or machinery and/or electronic operating line.
Summary of the invention
Therefore task of the present invention is, proposes a kind of multiple-speed gear-box that starts put forward type, and it has the efficiency of improvement and the structure consumes of minimizing, and has the switching member arranging in its operating aspect optimization.
According to the present invention, this task solves by the feature of claim 1.Other improvement project is drawn by dependent claims, specification and accompanying drawing.
Accordingly, a kind of multiple-speed gear-box planetary transmission of many gears in other words of the planetary gear construction mode for vehicle is proposed, its it comprise a housing, in this housing, accommodate four planetary gear set, four planetary gear set gear planes and preferably eight axles that can rotate and six switching members in other words.Realize multiple gears by operation switching member.
Obtain multiple-speed gear-box of the present invention by following manner: the first axle as drive end in other words live axle respectively with first and the sun gear of third planet gear train and be connected maybe and can connect with planet carrier and the housing of the first planetary gear set and the second planetary gear set respectively, the second axle as driven end in other words driven shaft be connected maybe and can connect with the gear ring of fourth planet gear train and the planet carrier of third planet gear train, the gear ring of the first planetary gear set is connected maybe and can connects with the sun gear of the second planetary gear set and the planet carrier of fourth planet gear train, second is connected maybe and can connects with the gear ring of third planet gear train, and the sun gear of fourth planet gear train can be connected with housing, multiple-speed gear-box according to the present invention based on switching member good can be from preferably high efficiency manipulation switching member more of outside proximity.In addition, by according to the present invention being connected between selected transmission element in advised multiple-speed gear-box, realized velocity ratio order and lower absolute rotating speed and relative rotation speed and less planetary gear set moment and the switching member moment optimized.In addition, arrange the meshing efficiency that is improved with low structure consumes and little member load by gear train, thereby reduced in an advantageous manner cost of production and the weight of multiple-speed gear-box.
Term " connection " is especially interpreted as that at this element being connected is just in time connected to each other directly via an axle.
Term " can connect " and especially represent to be connected to each other via axle by element connected to one another, and this axle can be interrupted sometimes by least one switching member.
In addition, in multiple-speed gear-box according to the present invention on the one hand by by break as switching member and on the other hand by by being positioned external shaft, preferably the clutch on drive end and driven end realizes as switching member the accessibility that switching member is good.
Each planetary gear set is observed vertically can be with the order setting of the first planetary gear set, the second planetary gear set, third planet gear train and fourth planet gear train, be preferably configured as negative transmission ratio planetary gear train in this first, third and fourth planetary gear set, and the second planetary gear set is preferably configured as positive drive and compares planetary gear set.But situation about allowing in the connectivity next one or multiple negative transmission ratio planetary gear trains are convertible into positive drive and compare planetary gear set, if being connected with gear ring, planet carrier changes and the value raising 1 of fixed drive ratio simultaneously, otherwise, also positive drive can be configured to negative transmission ratio planetary gear train than planetary gear set.Known negative transmission ratio planetary gear train has the planetary pinion that can support rotationally on planet carrier, these planetary pinions engage with sun gear and the gear ring of this planetary gear set, thereby gear ring is fixed and has and the sense of rotation of sun gear direction of rotation sun gear rotates in the situation that at planet carrier.Known positive drive have on its planet carrier than planetary gear set can support rotationally and the planetary pinion in ingear inner side and outside each other, the sun gear of this planetary gear set engages with the planetary pinion of inner side and the gear ring of this planetary gear set and the planetary pinion in outside engage.Therefore gear ring is fixed and has a sense of rotation identical with sun gear sense of rotation sun gear rotates in the situation that at planet carrier.
Connect to each other other order that also can realize planetary gear set remain unchanged in the situation that at each element.
In the scope of favourable mode of execution of the present invention, can specify, preferably the first switching member can have different positions, the gear train alternative that these position formation effects are identical.Substantially replace the connection setting that can get loose between live axle and the sun gear of third planet gear train to be fixedly connected with at this, in this multiple-speed gear-box, on the position of other the pre-regulation between transmission element, realize the connection that can get loose via the first switching member at this moment.For example can the connection that can get loose be set in other words between driven shaft at the gear ring of the planet carrier of third planet gear train and fourth planet gear train.Also can expect, second and the gear ring of third planet gear train between the connection that can get loose is set.Also can the connection that can get loose be set in other words between live axle at the planet carrier of the first and second planetary gear set.Finally also can expect, be the gear ring of the first planetary gear set and the planet carrier of fourth planet gear train on the one hand and be, between the sun gear of the second planetary gear set, the connection that can get loose is set on the other hand.
Term " switching member " can be regarded as the connection set that can be switched between two elements of speed changer, and the torque that will transmit between these two elements connects by force closure the sealed connection or transmit by the sealed connection of shape of rubbing in other words.In the time that two elements of the connection set that can be switched are constructed to be permeable to rotate, switching member is known as clutch and when only when rotation in two elements of the connection set that can be switched, this switching member is known as break.In addition, the geometric position of each switching member or order also can freely be selected, as long as the connectivity of these elements allows.Each element can move arbitrarily in its position in this way.The embodiment of force closure switching member is lamella clutch or chip break, band brake, cone clutch or cone stop, magnetic clutch, magnetic powder clutch and electrorheological clutch.The embodiment of the sealed switching member of shape is jaw clutch or dental inlay break and tooth clutch.
Preferably especially the first switching member and the 5th switching member can construct based on its feature the sealed switching member that is shaped, and realize significantly and reduce and consume thus.
Can be based on drive end and driven end according to multiple-speed gear-box as suggested in the present invention coaxially arranged for realize standard drive unit at vehicle.But also can on vehicle, realize preposition-horizontal mounting type with planetary transmission, its mode is, the geometrical arrangements of the each element of change planetary transmission and the therefore layout of order, for example each planetary gear set and switching member---as long as the connectivity of these transmission element allows, for example drive end and driven end are staggered each other and arrange.
In multiple-speed gear-box of the present invention, can use fluid torque converter or hydraulic couplers as initiating element.Also can expect using additional starting clutch or integrated starting clutch or starting break.In addition, at least one axle, motor or other power source/power source are set therein.On at least one axle, with respect to housing or another axle, overrunning clutch is set therein in addition.
Brief description of the drawings
Describe the present invention in detail below with reference to accompanying drawing.Accompanying drawing is as follows:
Fig. 1 illustrates the replacement position according to the schematic diagram of the first mode of execution of multiple-speed gear-box of the present invention and its with the first switching member that four kinds of signals show;
Fig. 2 illustrates the schematic diagram of the second mode of execution of multiple-speed gear-box;
Fig. 3 illustrates the schematic diagram of the third mode of execution of multiple-speed gear-box;
Fig. 4 illustrates the schematic diagram of the 4th kind of mode of execution of multiple-speed gear-box;
Fig. 5 illustrates the schematic diagram of the 5th kind of mode of execution of multiple-speed gear-box;
Fig. 6 illustrates the gearshift sketch for the different mode of executions of multiple-speed gear-box.
Embodiment
In accompanying drawing, illustrate for vehicle according to the multiple-speed gear-box of planetary gear construction mode of the present invention, as the different mode of executions of automatic transmission.
Irrelevant with corresponding mode of execution, multiple-speed gear-box comprises a housing 9, there is four planetary gear set RS1, RS2, RS3, RS4 and six switching member A, B, C, D, E, F and eight axles that can rotate 1,2,3,4,5,6,7,8,8A, 8B, 8C, 8D, can be regarded as one or more members of arbitrary structures form at this term " axle ", it connects at least two elements of coupling multistage speed changer in other words.In advised multiple-speed gear-box, the housing coupling of regulation is realized by the switching member that is configured to break, and therefore fixing housing coupling is not set.
For example use multiple negative transmission ratio planetary gear trains and a positive drive than planetary gear set as planetary gear set, in illustrated embodiment, the first, third and fourth planetary gear set RS1, RS3, RS4 are configured to respectively negative transmission ratio planetary gear train and the second planetary gear set RS2 and are configured to positive drive and compare planetary gear set.In addition, first, second, and third switching member A, B, C are configured to respectively clutch and the 4th, the 5th and the 6th switching member D, E, F and are configured to respectively break.For example form chip break or lamella clutch at this, preferably the first switching member A and the 5th switching member E are configured to dental inlay switching member to reduce consumption.
Specify in multiple-speed gear-box by the present invention, the first axle 1 is directly connected or can indirectly connects with the sun gear SO3 of third planet gear train RS3 as drive end An.This represents, the first axle 1 do not have in other element situation, be directly connected with sun gear SO3 or the first axle 1 indirectly, for example can be connected with sun gear SO3 via the first switching member A with via another axle 8 with getting loose.Other the first axle 1 can be connected indirectly with the planet carrier PT2 of the planet carrier PT1 of the sun gear SO1 of the first planetary gear set RS1 and the first planetary gear set RS1 and the second planetary gear set RS1, RS2.The second axle 2 is directly connected with the gear ring HO4 of fourth planet gear train RS4 as driven end Ab.This expression, the second axle 2 is not having in other element situation, is directly being connected with gear ring HO4.Other the second axle 2 is directly connected or can indirectly connects with the planet carrier PT3 of third planet gear train RS3.This represents, the second axle 2 is in the situation that there is no other element, be directly connected with planet carrier PT3 or the second axle 2 for example can be connected with planet carrier PT3 via the first switching member A with via another axle 8A with getting loose.In addition the sun gear SO4 of the sun gear SO1 of the first planetary gear set RS1 and planet carrier PT1 and fourth planet gear train RS4 can be connected with housing 9 respectively.In addition the gear ring HO1 of the first planetary gear set RS1 is connected with the planet carrier PT4 of fourth planet gear train RS4 and is connected maybe and can connects with the sun gear SO2 of the second planetary gear set RS2.The gear ring HO3 of the gear ring HO2 of the second last planetary gear set RS2 and third planet gear train RS3 is connected to each other and maybe can be connected to each other.
Produced four positions that effect is identical of the first switching member A by described connection possibility.Replace position according to shown in five of the multiple-speed gear-box of Fig. 1 to 5 kinds of different mode of executions.
Fig. 1 illustrates the first mode of execution, wherein marks four other positions of the first switching member A with mark 1. (corresponding to according to the second mode of execution of Fig. 2), mark 2. (corresponding to according to the third mode of execution of Fig. 3), mark 3. (corresponding to according to the 4th of Fig. 4 the kind of mode of execution) and mark 4. (corresponding to according to the 5th of Fig. 5 the kind of mode of execution).
Shown in Fig. 1 according to specifying in the gear train of multiple-speed gear-box the first mode of execution, the first axle 1 can be via being configured to the first switching member A of clutch and being connected with the sun gear SO3 of third planet gear train RS3 via the 8th axle 8, this expression, the first axle 1 can be connected with sun gear SO3 with getting loose.In addition the first axle 1 is via being configured to the second switching member B of clutch and can being connected in other words and can connecting with getting loose with the planet carrier PT1 of the first planetary gear set RS1 and the planet carrier PT2 of the second planetary gear set RS2 via the 3rd axle 3, the planet carrier PT1 of the first planetary gear set RS1 via the 3rd axle 3 with can be connected with housing 9 via the 5th switching member E that is configured to break with getting loose.In addition, the first axle 1 is via being configured to the 3rd switching member C of clutch and can being connected with the sun gear SO1 of the first planetary gear set RS1 via the 4th axle 4 with getting loose, the sun gear SO1 of the first planetary gear set RS1 via the 4th axle 4 with can be connected with housing 9 via the 4th switching member D that is configured to break with getting loose.The second axle 2 is connected with the gear ring HO4 of fourth planet gear train RS4 and the planet carrier PT3 of third planet gear train RS3.The gear ring HO1 of the first planetary gear set RS1 is connected with the sun gear SO2 of the second planetary gear set RS2 and the planet carrier PT4 of fourth planet gear train RS4 via the 7th axle 7.The gear ring HO2 of the second planetary gear set RS2 is connected with the gear ring HO3 of third planet gear train RS3 via the 6th axle 6.The sun gear SO4 of fourth planet gear train RS4 via the 5th axle 5 with can be connected with housing 9 via the 6th switching member F that is configured to break with getting loose.
Shown in Fig. 2 according to specifying in the gear train of the second mode of execution of multiple-speed gear-box, the first axle 1 is connected with the sun gear SO3 of third planet gear train RS3.In addition, the first axle 1 is via being configured to the second switching member B of clutch and can being connected in other words and can connecting with getting loose with the planet carrier PT1 of the first planetary gear set RS1 and the planet carrier PT2 of the second planetary gear set RS2 via the 3rd axle 3, the planet carrier PT1 of the first planetary gear set RS1 via the 3rd axle 3 with can be connected with housing 9 via the 5th switching member E that is configured to break with getting loose.In addition, the first axle 1 is via being configured to the 3rd switching member C of clutch and can being connected with the sun gear SO1 of the first planetary gear set RS1 via the 4th axle 4 with getting loose, the sun gear SO1 of the first planetary gear set RS1 via the 4th axle 4 with can be connected with housing 9 via the 4th switching member D that is configured to break with getting loose.The second axle 2 is connected with the gear ring HO4 of fourth planet gear train RS4.In addition, the second axle 2 is via being configured to the first switching member A of clutch and can being connected with the planet carrier PT3 of third planet gear train RS3 via axle 8A with getting loose.The gear ring HO1 of the first planetary gear set RS1 is connected with the sun gear SO2 of the second planetary gear set RS2 and the planet carrier PT4 of fourth planet gear train RS4 via the 7th axle 7.The gear ring HO2 of the second planetary gear set RS2 is connected with the gear ring HO3 of third planet gear train RS3 via the 6th axle 6.In addition, the sun gear SO4 of fourth planet gear train RS4 via the 5th axle 5 with can be connected with housing via the 6th switching member F that is configured to break with getting loose.
Shown in Fig. 3 according to specifying in the gear train of the third mode of execution of multiple-speed gear-box, the first axle 1 is connected with the sun gear SO3 of third planet gear train RS3.In addition, the first axle 1 is via being configured to the second switching member B of clutch and can being connected with the planet carrier PT1 of the first planetary gear set RS1 and the planet carrier PT2 of the second planetary gear set RS2 via the 3rd axle 3 with getting loose, the planet carrier PT1 of the first planetary gear set RS1 via the 3rd axle 3 with can be connected with housing 9 via the 5th switching member E that is configured to break with getting loose.In addition, the first axle 1 is via being configured to the 3rd switching member C of clutch and can being connected with the sun gear SO1 of the first planetary gear set RS1 via the 4th axle 4 with getting loose, the sun gear SO1 of the first planetary gear set RS1 via the 4th axle 4 with can be connected with housing 9 via the 4th switching member D that is configured to break with getting loose.The second axle 2 is connected with the gear ring HO4 of fourth planet gear train RS4 and the planet carrier PT3 of third planet gear train RS3.The gear ring HO1 of the first planetary gear set RS1 is connected with the sun gear SO2 of the second planetary gear set RS2 and the planet carrier PT4 of fourth planet gear train RS4 via the 7th axle 7.The gear ring HO2 of the second planetary gear set RS2 via the 6th axle 6 with via being configured to the first switching member A of clutch and can being connected with the gear ring HO3 of third planet gear train RS3 via the 8th axle 8B with getting loose.The sun gear SO4 of fourth planet gear train RS4 via the 5th axle 5 with can be connected with housing 9 via the 6th switching member F that is configured to break with getting loose.
Shown in Fig. 4 according to specifying in the gear train of the 4th of multiple-speed gear-box the kind of mode of execution, the first axle 1 is connected with the sun gear SO3 of third planet gear train RS3.In addition, the first axle 1 is via being configured to the second switching member B of clutch and being connected with the planet carrier PT1 of the first planetary gear set RS1 via the 3rd axle 3, the planet carrier PT1 of the first planetary gear set RS1 via the 3rd axle 3 with can be connected with housing 9 via the 5th switching member E that is configured to break with getting loose.The planet carrier PT2 of the second planetary gear set RS2 via the 3rd axle 3 with via being configured to the first switching member A of clutch and can being connected with the planet carrier PT1 of the first axle 1 and the first planetary gear set RS1 via the 8th axle 8C with getting loose.In addition, the first axle 1 is via being configured to the 3rd switching member C of clutch and can being connected with the sun gear SO1 of the first planetary gear set RS1 via the 4th axle 4 with getting loose, the sun gear SO1 of the first planetary gear set RS1 via the 4th axle 4 with can be connected with housing 9 via the 4th switching member D that is configured to break with getting loose.The second axle 2 is connected with the gear ring HO4 of fourth planet gear train RS4 and the planet carrier PT3 of third planet gear train RS3.The gear ring HO1 of the first planetary gear set RS1 is connected with the sun gear (SO2) of the second planetary gear set RS2 and the planet carrier PT4 of fourth planet gear train RS4 via the 7th axle 7.The gear ring HO2 of the second planetary gear set RS2 is connected with the gear ring HO3 of third planet gear train RS3 via the 6th axle 6.Finally, the sun gear SO4 of fourth planet gear train RS4 via the 5th axle 5 with can be connected with housing 9 via the 6th switching member F that is configured to break with getting loose.
Shown in Fig. 5 according to specifying in the gear train of the 5th kind of mode of execution, the first axle 1 is connected with the sun gear SO3 of third planet gear train RS3.In addition, the first axle 1 is via being configured to the second switching member B of clutch and can being connected with the planet carrier PT1 of the first planetary gear set RS1 and the planet carrier PT2 of the second planetary gear set RS2 via the 3rd axle 3 with getting loose, the planet carrier PT1 of the first planetary gear set RS1 via the 3rd axle 3 with can be connected with housing 9 via the 5th switching member E that is configured to break with getting loose.In addition, the first axle 1 is via being configured to the 3rd switching member C of clutch and can being connected with the sun gear SO1 of the first planetary gear set RS1 via the 4th axle 4 with getting loose, the sun gear SO1 of the first planetary gear set RS1 via the 4th axle 4 with can be connected with housing 9 via the 4th switching member D that is configured to break with getting loose.The second axle 2 is connected with the gear ring HO4 of fourth planet gear train RS4 and the planet carrier PT3 of third planet gear train RS3.The gear ring HO1 of the first planetary gear set RS1 is connected with the planet carrier PT4 of fourth planet gear train RS4 via the 7th axle 7.The planet carrier PT4 of the gear ring HO1 of the first planetary gear set RS1 and fourth planet gear train RS4 is via being configured to the first switching member A of clutch and can being connected with the sun gear SO2 of the second planetary gear set RS2 via the 8th axle 8D with getting loose.The gear ring of the second planetary gear set RS2 is connected with the gear ring HO3 of third planet gear train RS3 via the 6th axle 6.The sun gear SO4 of fourth planet gear train RS4 via the 5th axle 5 with can be connected with housing 9 via the 6th switching member F that is configured to break with getting loose.
Gearshift sketch for the identical gear train of the effect shown in Fig. 1～5 shown in Figure 6.In gearshift sketch, being depicted as and realizing switching member A, B, C, D, E, the F that different gears want closure will activate in other words with form, is corresponding speed ratio interval between each gear explanation velocity ratio i and different gear
.Reverse gear R except nine regulation forward gear G1, G2, G3, G4, G5, G6, G7, G8, G9 and a regulation, also specify that another additional shift combination Z may gear as another.As preferred fixed drive ratio (Stand ü bersetzung), in the first planetary gear set RS1, adoptable value is about i
0=-3.850, in the second planetary gear set RS2, adoptable value is about i
0=-1.670, in third planet gear train RS3, adoptable value is about i
0=-2.388 and in fourth planet gear train RS4 adoptable value be about i
0=-3.498.In addition, from this gearshift sketch, for switching respectively closed three switching members of a gear.Two switching members that will simultaneously switch are only set in order to shift gears.
Particularly, from according to the gearshift sketch of Fig. 6, in order to realize the first forward gear G1 closed the first switching member A, the 3rd switching member C and the 5th switching member E.In order to realize the second forward gear G2 closed the first switching member A, the 4th switching member D and the 5th switching member E.Closed the first switching member A, the 5th switching member E and the 6th switching member F in the 3rd forward gear G3.In order to realize the 4th forward gear G4 closed the first switching member A, the 4th switching member D and the 6th switching member F.Closed the first switching member A, the 3rd switching member C and the 6th switching member F in the 5th forward gear G5.Closed the first switching member A, the second switching member B and the 6th switching member F in the 6th forward gear G6.In order to realize the 7th forward gear G7 closed the first switching member A, the second switching member B and the 3rd switching member C.In order to realize the 8th forward gear G8 closed the second switching member B, the 3rd switching member C and the 6th switching member F.In order to realize the 9th forward gear G9 closed the second switching member B, the 4th switching member D and the 6th switching member F.In order to realize the R that reverses gear closed the 3rd switching member C, the 5th switching member E and the 6th switching member F.Closed the first switching member A, the second switching member B and the 4th switching member D in additional gear Z.
Reference numerals list
1 the first axle as drive end
2 the second axles as driven end
3 the 3rd axles
4 the 4th axles
5 the 5th axles
6 the 6th axles
7 the 7th axles
8,8A, 8B, 8C, 8D the 8th axle
9 housings
A the first switching member
B the second switching member
C the 3rd switching member
D the 4th switching member
E the 5th switching member
F the 6th switching member
RS1 the first planetary gear set
RS2 the second planetary gear set
RS3 third planet gear train
RS4 fourth planet gear train
The sun gear of SO1 the first planetary gear set
The planet carrier of PT1 the first planetary gear set
The gear ring of HO1 the first planetary gear set
The sun gear of SO2 the second planetary gear set
The planet carrier of PT2 the second planetary gear set
The gear ring of HO2 the second planetary gear set
The sun gear of SO3 third planet gear train
The planet carrier of PT3 third planet gear train
The gear ring of HO3 third planet gear train
The sun gear of SO4 fourth planet gear train
The planet carrier of PT4 fourth planet gear train
The gear ring of HO4 fourth planet gear train
G1 the first forward gear
G2 the second forward gear
G3 the 3rd forward gear
G4 the 4th forward gear
G5 the 5th forward gear
G6 the 6th forward gear
G7 the 7th forward gear
G8 the 8th forward gear
G9 the 9th forward gear
R reverses gear
Z adds gear
1. first replacement position of the first switching member
2. replace position for second of the first switching member
3. replace position for the 3rd of the first switching member the
4. replace position for the 4th of the first switching member the
I velocity ratio
I
0the fixed drive ratio of planetary gear set
speed ratio interval
Claims (12)
1. for the multiple-speed gear-box of the planetary gear construction mode of vehicle, it comprises a housing (9), is provided with four planetary gear set (RS1 in this housing, RS2, RS3, and multiple axle (1 RS4), 2, 3, 4, 5, 6, 7, 8, 8A, 8B, 8C, 8D) and six switching member (A, B, C, D, E, F), can realize multiple gears by operation switching member, it is characterized in that, the first axle (1) is directly connected or can indirectly connects with the sun gear (SO3) of third planet gear train (RS3) as drive end (An), can indirectly be connected with the sun gear (SO1) of the first planetary gear set (RS1), can indirectly be connected with the planet carrier (PT1) of the first planetary gear set (RS1) and can indirectly be connected with the planet carrier (PT2) of the second planetary gear set (RS2), the second axle (2) is directly connected with the gear ring (HO4) of fourth planet gear train (RS4) as driven end (Ab) and is directly connected or can indirectly connects with the planet carrier (PT3) of third planet gear train (RS3), the sun gear (SO4) of the sun gear (SO1) of the first planetary gear set (RS1) and planet carrier (PT1) and fourth planet gear train (RS4) can be connected with housing (9) respectively, the gear ring (HO1) of the first planetary gear set (RS1) is connected with the planet carrier (PT4) of fourth planet gear train (RS4) and is connected maybe and can connects with the sun gear (SO2) of the second planetary gear set (RS2), and the gear ring (HO2) of the second planetary gear set (RS2) and the gear ring (HO3) of third planet gear train (RS3) are connected to each other and maybe can be connected to each other.
2. according to the multiple-speed gear-box of claim 1, it is characterized in that, the first axle (1) can be via being configured to first switching member (A) of clutch and being connected with the sun gear (SO3) of third planet gear train (RS3) via the 8th axle (8), the first axle (1) can be via being configured to second switching member (B) of clutch and being connected with the planet carrier (PT1) of the first planetary gear set (RS1) and the planet carrier (PT2) of the second planetary gear set (RS2) via the 3rd axle (3), the planet carrier (PT1) of the first planetary gear set (RS1) can via the 3rd axle (3) be connected with housing (9) via the 5th switching member (E) that is configured to break, the first axle (1) can be via being configured to the 3rd switching member (C) of clutch and being connected with the sun gear (SO1) of the first planetary gear set (RS1) via the 4th axle (4), the sun gear (SO1) of the first planetary gear set (RS1) can via the 4th axle (4) be connected with housing (9) via the 4th switching member (D) that is configured to break, the second axle (2) is connected with the gear ring (HO4) of fourth planet gear train (RS4) and the planet carrier (PT3) of third planet gear train (RS3), the gear ring (HO1) of the first planetary gear set (RS1) is connected with the sun gear (SO2) of the second planetary gear set (RS2) and the planet carrier (PT4) of fourth planet gear train (RS4) via the 7th axle (7), the gear ring (HO2) of the second planetary gear set (RS2) is connected with the gear ring (HO3) of third planet gear train (RS3) via the 6th axle (6), and the sun gear (SO4) of fourth planet gear train (RS4) can via the 5th axle (5) be connected (Fig. 1) via the 6th switching member (F) that is configured to break with housing (9).
3. according to the multiple-speed gear-box of claim 1, it is characterized in that, the first axle (1) is connected with the sun gear (SO3) of third planet gear train (RS3), the first axle (1) can be via being configured to second switching member (B) of clutch and being connected with the planet carrier (PT1) of the first planetary gear set (RS1) and the planet carrier (PT2) of the second planetary gear set (RS2) via the 3rd axle (3), the planet carrier (PT1) of the first planetary gear set (RS1) via the 3rd axle (3) be connected with housing (9) via the 5th switching member (E) that is configured to break, the first axle (1) can be via being configured to the 3rd switching member (C) of clutch and being connected with the sun gear (SO1) of the first planetary gear set (RS1) via the 4th axle (4), the sun gear (SO1) of the first planetary gear set (RS1) can via the 4th axle (4) be connected with housing (9) via the 4th switching member (D) that is configured to break, the second axle (2) is connected with the gear ring (HO4) of fourth planet gear train (RS4), the second axle (2) can be via being configured to first switching member (A) of clutch and being connected with the planet carrier (PT3) of third planet gear train (RS3) via the 8th axle (8A), the gear ring (HO1) of the first planetary gear set (RS1) can be connected with the sun gear (SO2) of the second planetary gear set (RS2) and the planet carrier (PT4) of fourth planet gear train (RS4) via the 7th axle (7), the gear ring (HO2) of the second planetary gear set (RS2) is connected with the gear ring (HO3) of third planet gear train (RS3) via the 6th axle (6), and the sun gear (SO4) of fourth planet gear train (RS4) can via the 5th axle (5) be connected (Fig. 2) via the 6th switching member (F) that is configured to break with housing (9).
4. according to the multiple-speed gear-box of claim 1, it is characterized in that, the first axle (1) is connected with the sun gear (SO3) of third planet gear train (RS3), the first axle (1) can be via being configured to second switching member (B) of clutch and being connected with the planet carrier (PT1) of the first planetary gear set (RS1) and the planet carrier (PT2) of the second planetary gear set (RS2) via the 3rd axle (3), the planet carrier (PT1) of the first planetary gear set (RS1) can via the 3rd axle (3) be connected with housing (9) via the 5th switching member (E) that is configured to break, the first axle (1) can be via being configured to the 3rd switching member (C) of clutch and being connected with the sun gear (SO1) of the first planetary gear set (RS1) via the 4th axle (4), the sun gear (SO1) of the first planetary gear set (RS1) can via the 4th axle (4) be connected with housing (9) via the 4th switching member (D) that is configured to break, the second axle (2) is connected with the gear ring (HO4) of fourth planet gear train (RS4) and the planet carrier (PT3) of third planet gear train (RS3), the gear ring (HO1) of the first planetary gear set (RS1) is connected with the sun gear (SO2) of the second planetary gear set (RS2) and the planet carrier (PT4) of fourth planet gear train (RS4) via the 7th axle (7), the gear ring (HO2) of the second planetary gear set (RS2) can via the 6th axle (6) with via being configured to first switching member (A) of clutch and being connected with the gear ring (HO3) of third planet gear train (RS3) via the 8th axle (8B), and the sun gear (SO4) of fourth planet gear train (RS4) can via the 5th axle (5) be connected (Fig. 3) via the 6th switching member (F) that is configured to break with housing (9).
5. according to the multiple-speed gear-box of claim 1, it is characterized in that, the first axle (1) is connected with the sun gear (SO3) of third planet gear train (RS3), the first axle (1) can be via being configured to second switching member (B) of clutch and being connected with the planet carrier (PT1) of the first planetary gear set (RS1) via the 3rd axle (3), the planet carrier (PT1) of the first planetary gear set (RS1) can via the 3rd axle (3) be connected with housing (9) via the 5th switching member (E) that is configured to break, the planet carrier (PT2) of the second planetary gear set (RS2) can via the 3rd axle (3) with via being configured to first switching member (A) of clutch and being connected with the planet carrier (PT1) of the first axle (1) and the first planetary gear set (RS1) via the 8th axle (8C), the first axle (1) can be via being configured to the 3rd switching member (C) of clutch and being connected with the sun gear (SO1) of the first planetary gear set (RS1) via the 4th axle (4), the sun gear (SO1) of the first planetary gear set (RS1) can via the 4th axle (4) be connected with housing (9) via the 4th switching member (D) that is configured to break, the second axle (2) is connected with the gear ring (HO4) of fourth planet gear train (RS4) and the planet carrier (PT3) of third planet gear train (RS3), the gear ring (HO1) of the first planetary gear set (RS1) is connected with the sun gear (SO2) of the second planetary gear set (RS2) and the planet carrier (PT4) of fourth planet gear train (RS4) via the 7th axle (7), the gear ring (HO2) of the second planetary gear set (RS2) is connected with the gear ring (HO3) of third planet gear train (RS3) via the 6th axle (6), and the sun gear (SO4) of fourth planet gear train (RS4) can via the 5th axle (5) be connected (Fig. 4) via the 6th switching member (F) that is configured to break with housing (9).
6. according to the multiple-speed gear-box of claim 1, it is characterized in that, the first axle (1) is connected with the sun gear (SO3) of third planet gear train (RS3), the first axle (1) can be via being configured to second switching member (B) of clutch and being connected with the planet carrier (PT1) of the first planetary gear set (RS1) and the planet carrier (PT2) of the second planetary gear set (RS2) via the 3rd axle (3), the planet carrier (PT1) of the first planetary gear set (RS1) can via the 3rd axle (3) be connected with housing (9) via the 5th switching member (E) that is configured to break, the first axle (1) can be via being configured to the 3rd switching member (C) of clutch and being connected with the sun gear (SO1) of the first planetary gear set (RS1) via the 4th axle (4), the sun gear (SO1) of the first planetary gear set (RS1) can via the 4th axle (4) be connected with housing (9) via the 4th switching member (D) that is configured to break, the second axle (2) is connected with the gear ring (HO4) of fourth planet gear train (RS4) and the planet carrier (PT3) of third planet gear train (RS3), the gear ring (HO1) of the first planetary gear set (RS1) is connected with the planet carrier (PT4) of fourth planet gear train (RS4) via the 7th axle (7) and can be via being configured to first switching member (A) of clutch and being connected with the sun gear (SO2) of the second planetary gear set (RS2) via the 8th axle (8D), the gear ring (HO2) of the second planetary gear set (RS2) can be connected with the gear ring (HO3) of third planet gear train (RS3) via the 6th axle (6), and the sun gear (SO4) of fourth planet gear train (RS4) can via the 5th axle (5) be connected (Fig. 5) via the 6th switching member (F) that is configured to break with housing (9).
7. according to the multiple-speed gear-box of one of the claims, it is characterized in that, at least nine forward gears (G1, G2, G3, G4, G5, G6, G7, G8, G9, Z) and at least one reverse gear (R) can be switched on, and in order to realize each gear, at least three switching members in described six switching members (A, B, C, D, E, F) are closed.
8. according to the multiple-speed gear-box of one of the claims, it is characterized in that, the first switching member (A), the second switching member (B) and the 3rd switching member (C) are configured to respectively clutch, and the 4th switching member (D), the 5th switching member (E) and the 6th switching member (F) are configured to respectively break.
9. multiple-speed gear-box according to Claim 8, is characterized in that, the first switching member (A) and/or the 5th switching member (E) the structure sealed switching member that is shaped.
10. according to the multiple-speed gear-box of one of the claims, it is characterized in that, the first planetary gear set (RS1), third planet gear train (RS3) and fourth planet gear train (RS4) are configured to respectively negative transmission ratio planetary gear, and the second planetary gear set (RS2) is configured to positive drive and compares planetary gear set.
11. according to the multiple-speed gear-box of one of the claims, it is characterized in that, by the 5th switching member (E) of closure, the 3rd switching member (C) and the first switching member (A) are realized the first forward gear (G1), by the 5th switching member (E) of closure, the 4th switching member (D) and the first switching member (A) are realized the second forward gear (G2), by the 5th switching member (E) of closure, the 6th switching member (F) and the first switching member (A) are realized the 3rd forward gear (G3), by the 4th switching member (D) of closure, the 6th switching member (F) and the first switching member (A) are realized the 4th forward gear (G4), by the 6th switching member (F) of closure, the 3rd switching member (C) and the first switching member (A) are realized the 5th forward gear (G5), by the 6th switching member (F) of closure, the second switching member (B) and the first switching member (A) are realized the 6th forward gear (G6), by second switching member (B) of closure, the 3rd switching member (C) and the first switching member (A) are realized the 7th forward gear (G7), by the 6th switching member (F) of closure, the second switching member (B) and the 3rd switching member (C) are realized the 8th forward gear (G8), by the 6th switching member (F) of closure, the 4th switching member (D) and the second switching member (B) are realized the 9th forward gear (G9), by the 5th switching member (E) of closure, the 6th switching member (F) and the 3rd switching member (C) are realized reverse gear (R), and by the 4th closed switching member (D), the second switching member (B) and the first switching member (A) are realized an optional forward gear (Z), and all remaining switching members are opened respectively.
12. according to the multiple-speed gear-box of claim 1, it is characterized in that, the planet carrier (PT1) of the first planetary gear set (RS1) is directly connected maybe and can connects with the planet carrier (PT2) of the second planetary gear set.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE102012203069A DE102012203069A1 (en) | 2012-02-29 | 2012-02-29 | Multi-speed planetary gearbox for a vehicle |
| DE102012203069.7 | 2012-02-29 | ||
| PCT/EP2013/050357 WO2013127548A1 (en) | 2012-02-29 | 2013-01-10 | Multi-stage planetary vehicle transmission |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN104136807A true CN104136807A (en) | 2014-11-05 |
| CN104136807B CN104136807B (en) | 2016-08-17 |
Family
ID=47598788
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201380010299.2A Expired - Fee Related CN104136807B (en) | 2012-02-29 | 2013-01-10 | Multiple-speed gear-box for the planetary gear construction mode of vehicle |
Country Status (5)
| Country | Link |
|---|---|
| US (1) | US8992373B2 (en) |
| EP (1) | EP2820329B1 (en) |
| CN (1) | CN104136807B (en) |
| DE (1) | DE102012203069A1 (en) |
| WO (1) | WO2013127548A1 (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
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| CN106687715A (en) * | 2014-11-25 | 2017-05-17 | 宝马股份公司 | Vehicle transmission with multiple gear ratios |
| CN106838152A (en) * | 2017-02-20 | 2017-06-13 | 彭建新 | A kind of multi-shifting speed variator of planetary gear construction mode |
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| DE102012203104A1 (en) * | 2012-02-29 | 2013-08-29 | Zf Friedrichshafen Ag | Multi-stage planetary gearbox for a vehicle |
| DE102012203936A1 (en) * | 2012-03-14 | 2013-09-19 | Zf Friedrichshafen Ag | Multi-speed transmission |
| DE102013205558B4 (en) | 2012-04-04 | 2022-06-09 | GM Global Technology Operations, LLC (n.d. Ges. d. Staates Delaware) | eleven-speed gearbox |
| DE102012206809B4 (en) * | 2012-04-25 | 2021-03-11 | Zf Friedrichshafen Ag | Multi-speed transmission |
| DE102013205380A1 (en) * | 2013-03-27 | 2014-10-02 | Zf Friedrichshafen Ag | Transmission for a motor vehicle |
| DE102013205388A1 (en) * | 2013-03-27 | 2014-10-02 | Zf Friedrichshafen Ag | Transmission for a motor vehicle |
| DE102013205384A1 (en) * | 2013-03-27 | 2014-10-02 | Zf Friedrichshafen Ag | Transmission for a motor vehicle |
| JP6219145B2 (en) * | 2013-08-30 | 2017-10-25 | アイシン・エィ・ダブリュ株式会社 | Multi-speed transmission |
| US9175748B2 (en) * | 2013-10-04 | 2015-11-03 | Ford Global Technologies, Llc | Multi-speed transmission |
| US9291244B2 (en) * | 2014-01-17 | 2016-03-22 | Ford Global Technologies, Llc | Nine speed automatic transmission |
| US10473190B2 (en) | 2016-09-28 | 2019-11-12 | Allison Transmission, Inc. | Multi-speed planetary transmission |
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| US9933045B1 (en) | 2016-09-28 | 2018-04-03 | Allison Transmission, Inc. | Multi-speed planetary transmission |
| US10234001B2 (en) | 2016-09-28 | 2019-03-19 | Allison Transmission, Inc. | Multi-speed planetary transmission |
| US10072735B2 (en) | 2016-09-28 | 2018-09-11 | Allison Transmission, Inc. | Multi-speed planetary transmission |
| US9927008B1 (en) | 2016-09-28 | 2018-03-27 | Allison Transmission, Inc. | Multi-speed planetary transmission |
| US10161486B2 (en) | 2016-09-28 | 2018-12-25 | Allison Transmission, Inc. | Multi-speed planetary transmission |
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| US10060511B2 (en) | 2016-09-28 | 2018-08-28 | Allison Transmission, Inc. | Multi-speed planetary transmission |
| US10174814B2 (en) | 2016-09-28 | 2019-01-08 | Allison Transmission, Inc. | Multi-speed planetary transmission |
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| US10323723B2 (en) | 2016-09-28 | 2019-06-18 | Allison Transmission, Inc. | Multi-speed planetary transmission |
| US9869377B1 (en) | 2016-09-28 | 2018-01-16 | Allison Transmission, Inc. | Multi-speed planetary transmission |
| US10060512B2 (en) | 2016-09-28 | 2018-08-28 | Allison Transmission, Inc. | Multi-speed planetary transmission |
| US10161484B2 (en) | 2016-09-28 | 2018-12-25 | Allison Transmission, Inc. | Multi-speed planetary transmission |
| CN117780872A (en) | 2019-10-07 | 2024-03-29 | 艾里逊变速箱公司 | Multi-speed planetary transmission |
| WO2021133631A1 (en) | 2019-12-23 | 2021-07-01 | Allison Transmission, Inc. | Multi-speed planetary transmission |
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- 2013-01-10 EP EP13700851.2A patent/EP2820329B1/en not_active Not-in-force
- 2013-01-10 CN CN201380010299.2A patent/CN104136807B/en not_active Expired - Fee Related
- 2013-01-10 WO PCT/EP2013/050357 patent/WO2013127548A1/en active Application Filing
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Also Published As
| Publication number | Publication date |
|---|---|
| DE102012203069A1 (en) | 2013-08-29 |
| US20150045174A1 (en) | 2015-02-12 |
| WO2013127548A1 (en) | 2013-09-06 |
| EP2820329B1 (en) | 2016-07-27 |
| US8992373B2 (en) | 2015-03-31 |
| EP2820329A1 (en) | 2015-01-07 |
| CN104136807B (en) | 2016-08-17 |
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